Modular multi-energy thermodynamic device

ABSTRACT

A system for simultaneously producing electricity, water at a first temperature, water at a second temperature greater than the first temperature, and water at a third temperature greater than the second temperature. The system can also optionally simultaneously provide a refrigerating fluid at a first evaporation temperature, and the refrigerating fluid at a second evaporation temperature.

FIELD OF THE INVENTION

The invention concerns a system or device of modular design comprisingat least one module generating electric current and one or more modulesfrom the following types: heat or refrigeration pumps or mixedheat/refrigeration pump modules, enabling the simultaneous production ofhot water, for example for heating buildings, very hot water, forexample domestic hot water, cold water, for example for airconditioning, optionally refrigerating fluid, typically forrefrigeration, and optionally electricity.

PRIOR ART

Systems are known composed of heat pumps actuated by internal combustionengines and using a steam-compression refrigeration cycle. The patentapplication EP 1 628 096 (LG Electronics Inc) describes such a system.These systems have been in common use in Japan for several years for airconditioning (cooling) in summer and heating in winter for buildingssuch as office premises or hotels, and the simultaneous production ofdomestic hot water. These systems are, the majority of the time,so-called direct expansion systems, that is to say they directly send arefrigerating fluid to individual internal units. These are generallyinstallations of the VRV (variable refrigerant volume) or VRO (variablerefrigerant output) type.

Such systems enable hot water to be produced, for example domestic hotwater, by virtue of the use of the heat released by the combustionengine in operation. However, one of the major drawbacks of the systemsis that the heat pump cannot function correctly by taking the necessaryheat from the air when the external temperature is less thanapproximately 10° C. since this causes frosting of the evaporator. Inpractice, in winter, the heat of the engine is used to heat theevaporator in order to enable the thermodynamic system to continue tofunction with good efficiency when the external temperature is below 10°C. (down to approximately −20° C.), the drawback being in this case thatwater at very high temperature is no longer produced and the overallefficiency of the system becomes fairly low.

In addition, the document EP 1 628 096 enables only water at a singletemperature to be supplied to the end user, the temperature of domestichot water, and when the system is in air conditioning mode. In avariant, the system comprises several units, in particular interiorunits and exterior units, connected by refrigerating fluid pipes. Inthis case also, only one water temperature can be supplied by thesystem, this being domestic hot water supplied in air conditioning modeof the system.

To remedy this drawback, the system described in the document EP 2 085721 of the applicant uses a cogeneration assembly connected to a heatpump designed so as to supply to the user, simultaneously, water atseveral different temperatures. However, the system described isdesigned for given refrigerating, heating and electrical capacity levelsspecific to a given application. The system is designed as a singleindivisible assembly and because of this it allows no flexibility indesign or use and must be completely resized for any new application.

Moreover, the existing systems have powers limited to maximum values ofaround 75 kW since they use car engines of limited power andrefrigeration components also not making it possible to function athigher powers.

Another drawback of the existing systems is that the sizing thereof mustbe adapted to the specific requirements of the user for water atdifferent temperatures. However, these requirements, with regard to boththe total quantity thereof and the distribution thereof over the variouswater temperatures, may vary according to the season or the lifestyle orin the course of a day. The systems according to the prior art firstlylack flexibility as to use thereof. Secondly, the correct sizing thereofaccording to the requirements of the user thereof in general requiresmade to measure design, or at least the possibility of selecting theappropriate system from a wide range of products of difference sizes.

The problem that the present invention sets out to solve is to remedythese drawbacks of the prior art.

SUBJECT MATTER OF THE INVENTION

A first subject matter is a system (1) for simultaneously producing veryhot water at temperature T2, hot water (14) at temperature T1 and/orcold water (13) at temperature T3, and electricity (20), and optionallyalso producing refrigerating fluid at evaporation temperature T4, and/orproducing refrigerating fluid at evaporation temperature T5, and saidsystem comprising at least one current-generating unit that compriseseither a combustion engine (2) connected to an alternator (18) or a fuelcell (22), each of the current generators also comprising a heatexchanger (8) producing very hot water at temperature T2, and saidsystem (1) or current generating unit optionally comprising one or moreother current generators, selected from the group comprising acombustion engine (2) connected to an alternator (18), a fuel cell (22),a photovoltaic solar panel (23) or a wind turbine,

and said system (1) also comprising at least one heat pump (3), or arefrigeration unit and optionally an electric accumulator (19),

said heat pump or said refrigeration unit being (i) either of the steamcompression type and then comprising at least one refrigerating fluidcompressor (17), a first heat exchanger (11, 66) situated at the suctionof the compressor (17) when the system (1) is in air conditioning mode,a pressure reducing valve (10), and second heat exchanger (12) placed atthe discharge of the compressor (17) when the system (1) is in airconditioning mode, and optionally a third heat exchanger (15) situatedat the discharge of the compressor (17) when the system (1) is in airconditioning mode and used for heating the hot water (14), (ii) or ofthe absorption type and then comprising an absorber (28), a circulationpump (30), a steam generator (29), a first heat exchanger (31) situatedat the inlet of said absorber (28), a pressure reducing valve (32) and asecond heat exchanger (33) situated at the outlet of said steamgenerator (29),

said system (1) being characterized in that

(a) the compressor (17) or the circulation pump (30) is driven by anelectric motor, which may be supplied by one of said current generators,and in that

(b) said system (1) comprises at least one module Pc, Pa referred to asa “heat pump module” (36, 37) or at least one module Pr referred to as a“refrigeration module” (36A) or at least one module Pm (36B) referred toas “mixed: heat and refrigeration pump” comprising,

(b1) if it is a case of a compression heat pump module Pc (36), each atleast one heat pump assembly comprising at least one refrigerating fluidcompressor (17), said first heat exchanger (11), said pressure reducingvalve (10), said second heat exchanger (12) and optionally said thirdheat exchanger (15);

(b2) if it is a case of an absorption heat pump module Pa (37), each anabsorber (28), said circulation pump (30), said steam generator (29),said first heat exchanger (31), said pressure reducing valve (32) andsaid second heat exchanger (33);

(b3) if it is a case of a refrigeration module Pr (36A), each at leastone refrigeration unit comprising at least one refrigerating fluidcompressor (17), said pressure reducing valve (10), said second heatexchanger (12) and optionally said third heat exchanger (15), as well asrefrigerating fluid pipes (16 a, 16 b) intended to be connected to anair/water refrigerating fluid exchanger (66) external to the module Pr(36A);

(b4) if it is a case of a mixed module Pm (36B), two units, one of theheat pump type and the other of the refrigeration type, wherein

the unit of the heat pump type comprises at least one refrigeratingfluid compressor (17), said first heat exchanger (11), said pressurereducing valve (10), said second heat exchanger (12) and optionally saidthird heat exchanger (15), and

the unit of the refrigeration type comprises at least one refrigeratingfluid compressor (17), said pressure reducing valve (10), said secondheat exchanger (12) and optionally said third heat exchanger (15) aswell as refrigerating fluid pipes (16 a, 16 b) intended to be connectedto an air/water refrigerating fluid exchanger (66) external the modulePm (36)

and in that said generating unit is included inside a generating module(G), said modules (G, Pc, Pa, Pr, Pm) each being provided with a frameand a unit forming an assembly interface produced so that said modules(G, Pc, Pa, Pr, Pm) can be assembled together, one after the other, andform a single unit.

System for simultaneously producing water at several temperatures, andoptionally refrigerating fluid, means a system able to produce andsupply to the user water and optionally refrigerating fluid at thespecified temperatures via suitable manifolds that connect the singleunit thus obtained to the plant of the user.

According to the invention, the number and type of modules is chosenaccording to the heating and/or refrigerating capacity and electricalpower necessary for the functioning of the system to adapt it to a givenapplication, as from the design thereof. Such a modular constructionoffers a broad pallet of design solutions for the system, by adaptingthe number and type of modules to each case of use. Moreover, the systemalso has flexibility in use since it takes account of a multiplicity ofenergies liable to supply the system, as well as a multiplicity ofenergy flows able to be produced by the system.

The system of the invention is modular in construction and makes itpossible to connect together several complex modules, in particularcogeneration and thermodynamic, while simplifying the interfaces inorder to obtain a unitary or single-piece assembly, preferably easilytransportable by lorry. Thus the complexity of the design isconcentrated inside the modules, the interfaces between modules beingsimplified to the maximum possible extent. The modules preferably haveframes of identical height and width for connection to each other bysuitable mechanical connection means.

This provides a standardization of the components, a reduction in thepurchase costs of the components by increasing volumes, a reduction inthe development time and a simplification of production.

A system will therefore be defined by choosing in an optimum fashion themodules that will be standardized, in particular through the internalfunctions thereof and the choice of interfaces in order to obtain asystem corresponding to the requirements of the end user. The system ofthe invention responds to the requirements of applications such as:

1) Heating, Domestic Hot Water and Air Conditioning of Service orResidential Buildings:

This gives rise to a variable thermal requirement according the sizes ofbuildings, according to the insulation levels thereof, according to thetypes thereof (hospital, hotels, retirement homes or offices) andaccording to the location thereof (north or south Europe). The preferredfluid being water at temperature T1 (heating), T2 (domestic hot water)and T3 (air conditioning). For some applications, there may besimultaneously air conditioning and heating requirements in certainparts of the building.

2) Heating, Domestic Hot Water, Air Conditioning and Supply ofRefrigeration Energy for Refrigeration Requirements for SupermarketApplications.

In addition to the points dealt with in the previous paragraph, there isadded the requirement for refrigerating capacity in the form ofrefrigerating fluid at temperatures T4 and T5 in variable proportionsaccording to the application.

3) Heating, Production of Electricity and Optionally Air Conditioning ofAgricultural Greenhouses:

There are in this case major heating requirements in the form of hotwater at temperatures T1 and T2 and often enjoying natural gas tariffsat a competitive cost. Any excess electricity may be resold.

4) Agricultural Biomass Plant Producing Biogas:

There is here local production of primary energy for covering heatingand electricity requirements with resale of the surplus thereof. Thereis a requirement for hot water at temperatures T1 and T2. The excesselectricity may be resold.

The various modules used by the system will be described and thecapacity supplied to the system will be given by way of examplehereinafter:

The cogeneration module (or generating module G) which enables heatcapacity to be generated in the form of hot water at temperature T2 andelectricity.

Internal functions of the module:

Each engine comprises one or two engines from the possible(non-limitative) choices of 2 liters and 4.6 liters.

The electric power can be used locally by the other modules or sentoutside with the electrical network of the customer.

The thermal output is transferred by a regulated valve to the centralwater pipes for hot water T1 or very hot water T2 according to therespective requirements of the application.

2-litre engine: up to 25 kW of electricity and simultaneously up to 35kW of heating capacity at temperature T2.

4.6-litre engine: up to 55 kW of electricity and simultaneously 80 kW ofheating capacity at temperature T2.

Minimum outputs: one 2-litre engine: 25 kW electrical and 35 kW heat.

Maximum outputs: two 4.6 liter engines: 110 kW electrical and 160 kWheat,

The reversible heat pump module (Pc) that enables hot water to beproduced at temperature T1 or cold water at temperature T3 using thecompression refrigeration cycle,

Internal functions of the module: each module comprises two independentrefrigeration units connected to the central water pipes, and aregulation system.

Each of the two units produces approximately 65 kW of cold water attemperature T3 or approximately 80 kW of hot water at temperature T1(non-simultaneously).

Each module of this type produces: approximately 130 kW of cold water attemperature T3 or approximately 160 kW of hot water at temperature T1(non-simultaneously).

The heat pump module with optional exchanger (Pc) simultaneouslyproducing hot water at temperature T1 and cold water at temperature T3using the compression refrigeration cycle.

Internal functions: Each module comprises two independent refrigerationunits connected to the central water pipes, and a regulation system.

Each of the two units can produce approximately 65 kW of cold water attemperature T3 or approximately 80 kW of hot water at temperature T1like the reversible heat pump module but it can also if necessaryproduce these two outputs simultaneously.

Each module of this type can therefore produce approximately 130 kW ofcold water at temperature T3 or approximately 160 kW of hot water attemperature T1 like the reversible heat pump module but it can also ifnecessary produce these two outputs simultaneously, that is to sayapproximately 130 kW of refrigeration energy in the form of cold waterat temperature T3 and approximately 160 kW of heat energy in the form ofhot water at temperature T1.

The refrigeration module (Pr) producing refrigerating fluid attemperature T4 or T5 using the compression refrigeration cycle.

Internal functions: each module comprises two independent refrigerationunits connected to the central refrigerating fluid pipes, and aregulation system.

Each of the two units can produce approximately 40 kW of refrigerationoutput in the form of refrigerating fluid at temperature T4 orapproximately 20 kW of refrigerating fluid at temperature T5.

Each module of this type can therefore produce approximately 80 kW ofrefrigeration output in the form of refrigerating fluid at temperatureT4 or approximately 40 kW of refrigerating fluid at temperature T5.

The mixed reversible heat/refrigeration pump module (Pm):

In addition, each of the above three modules (heat pump modules andrefrigeration module) is composed of two independent units fulfillingthe required function and it is therefore possible to have mixed modulescomprising for example a reversible heat pump unit and a refrigerationunit (example in FIG. 13):

There is therefore production of hot water at temperature T1(approximately 80 kW) or cold water at temperature T3 (approximately 65kW) and simultaneously production of refrigerating fluid at temperatureT4 (approximately 40 kW) or at temperature T5 (approximately 20 kW).

The absorption heat pump module (Pa): Production of hot water attemperature T1 using the absorption cycle. The heat output isapproximately 35 kW.

Advantageously, said unit forming an assembly interface comprises: amechanical interface, an electrical interface, and a fluid interface.

The system of the invention is modular in construction and comprises atleast one electric current generator and one or more so-called“production” modules, each comprising one or two heat-pump orrefrigeration units. System of modular construction means a systemcomprising at least two modules, each module comprising a frame forminga support for the components thereof, as well as means of mechanicalelectrical and fluid connection to the adjacent module. Preferably, themodules are produced so that, when connected, they have the same patternat least in one dimension (for example the width of the module) and,even more advantageously, in two dimensions (width and height). Aproduction module can comprise a heat-pump unit or a refrigeration unit.In an advantageous variant of the invention, a production module maycomprise two units of the same type, for example two heat-pump units ortwo refrigeration units, on a common frame. In another advantageousvariant of the invention, a production module is a mixed module, that isto say it comprises a heat-pump unit and refrigeration unit on a commonframe.

The interfaces between modules are limited to the maximum possibleextent and are of three types:

Mechanical interfaces: the modules have frames of identical heights andwidths in order to connect to each other by means of suitable mechanicalconnection means.

Electrical and electronic interfaces: the regulation particular to eachmodule makes it possible to limit the electronic interfaces (bycommunication bus mainly) and electrical interfaces (in particular thepower cables of the compressors).

Fluid interfaces, in particular hydraulic and refrigerating fluid: theyare situated at the same place for all the modules (preferably at thecentral part, such as the product shown in the drawings). Theyconstitute the path for passage and transfer of the heat energy to theoutside of the modular system of the invention.

Once these interfaces have been produced, the product is in the form ofa single block or single unit transportable in a single piece forexample by lorry.

Advantageously, up to six modules can be assembled together, includingone or two cogeneration modules (one cogeneration module at each end ofthe machine).

The electrical and thermal outputs of the various modules of thissingle-piece unit are then added together. One megawatt is for exampleapproached in terms of heat energy.

The electrical energy available will be used locally by the modules orreturned to the outside to the customer network according to respectiverequirements.

The regulation of the unit will then be aimed at the total energyoptimization of the machine.

Thus a system comprising six modules so defined advantageously fulfilsthe functions corresponding to the following applications:

1) Heating, domestic hot water and air conditioning of service orresidential buildings;

According to the respective power requirements firstly of airconditioning and heating (optionally simultaneous in a givenproportion), secondly domestic hot water and finally optional electricalbackup, it will be possible to configure one or two generating unitsassociated with heat pump modules possibly of a different type. This inorder to adhere to requirements with a single machine.

2) Heating, domestic hot water, air conditioning and supply ofrefrigeration energy for refrigeration requirements for supermarketapplications.

The response to multiple requirements will rely on the refrigerationmodules.

It will then be possible to have a. unit composed of one or twocogeneration modules associated with one or more refrigeration modulesthemselves supplemented by heat pump modules. The assembly affording anadapted, coherent and single-piece response to a complex problem.

3) Heating, production of electricity and optionally air conditioning ofagricultural greenhouses:

The maximum cogeneration power associated with heat-pump modules willtypically be found. The monobloc product avoids the use or constructionof a technical room.

4) Agricultural biomass plant producing biogas:

The available primary energy capacities are related to the size of themethanizers producing the biogas by biomass. This available power rangeis well suited to the cogeneration modules of the system of theinvention.

The system 1 of the invention also comprises at least one refrigerationmodule 36A and optionally an electric accumulator 19, said modulecomprising at least one refrigeration unit that is of the steamcompression type and then comprising at least one refrigerating fluidcompressor 17, a pressure reducing valve 10, a heat exchanger 12 placedat the discharge of the compressor 17 and optionally a third heatexchanger 15 situated at the discharge of the compressor 17 when thesystem 1 is also used for heating hot water 14, the system alsocomprising refrigerating fluid pipes intended to be connected to anexchanger 66 of the refrigerating fluid/air type situated outside themodule, or even outside the system typically, but not exclusively, inparticular for foodstuff refrigeration applications. The exchanger 66 isessential to the functioning. It is however not situated physically inthe module comprising the compressors. The exchanger 66 can be situatedin a specific isothermal module forming part of the modular-designsystem (cold chamber role external the building for example). Theexchanger 66 can also be situated at a distance from the modular-designsystem, in the enclosure of a building (application of the supermarkettype for example). More particularly, according to the invention in thiscase

(a) the compressor 17 is driven by an electric motor, which may besupplied by one of said current generators, and

(b) said system 1 comprises at least one module Pr referred to as a“refrigeration module” each comprising at least one refrigerating fluidcompressor 17, said pressure reducing valve 10, said heat exchanger 12optionally said heat exchanger 15, and refrigerating fluid pipes (16 a,16 b) intended to be connected to an exchanger 66 not being situatedphysically in the module, but being essential to the functioningthereof.

The current generator of the combustion engine type may be included in aso-called current generator module G; this module G may comprise one orseveral other current generators selected from combustion engines andfuel cells, or these other current generators may be integrated in asecond current generating module. The current generating module ormodules may advantageously comprise connections for connecting one orseveral external current sources such as a photovoltaic solar panel 23,a wind turbine or an electrical network. Said current generators may bealternating current or direct current generators. In an advantageousembodiment, the first current generator is a combustion engine 2connected to an alternator 18. In this case, the alternating current cansupply said compressor 17 with alternating current (some of it beingable to be introduced into an electrical network external to the system1), or it may be transformed into direct current to supply saidcompressor 17 functioning under direct current and/or to recharge theelectric accumulator 19. The same applies to the other currentgenerators if they produce alternating current (such as a combustionengine, a wind turbine or a turbine). If one of the other currentgenerators is a direct-current generator (for example the fuel cell 22or the photovoltaic panel 23), this direct current may be used eitherdirectly by the compressor 17, if the latter functions under directcurrent, and/or by the electric accumulator 19, or be transformed intoalternating current so as to be used by the compressor 17 functioningunder alternating current, and/or be introduced into an electricalnetwork external to the system 1.

Advantageously, said heat pump or refrigeration unit uses the steamcompression refrigeration cycle.

The system according to the invention is highly advantageously designedso as to be able to be supplied by an external electrical network inorder to cover, partly or wholly, the electrical requirements thereof,and so as to be able to send to said external electrical network atleast some of the electrical energy produced by said system.

A second subject matter of the invention is a method of regulating asystem according to the invention.

DESCRIPTION OF THE FIGURES

FIGS. 1 to 19 refer to the invention, particular embodiments of whichthey illustrate.

FIG. 1 shows an outline diagram of the system according to theinvention, in the case where the alternating current generator is acombustion engine connected to an alternator and the heat pump uses thesteam compression refrigeration cycle.

FIG. 2 shows an outline diagram of the system according to theinvention, in the case where the alternating current generator is aphotovoltaic solar panel or a fuel cell, connected to a DC to ACconverter, and the heat pump uses the steam compression refrigerationcycle.

FIG. 3 presents the energy efficiency of the system according to theinvention in the case of the heat pump compared with the efficiencies ofvarious systems of the prior art.

FIG. 4 shows an outline diagram of the system according to theinvention, in the case where the alternating current generator is acombustion engine connected to an alternator and the refrigerationmodule uses the steam compression refrigeration cycle.

FIG. 5 shows an outline diagram of a system of the invention accordingto a variant of the invention, the system comprising several currentgenerating modules connected to several heat pump modules.

FIG. 6 shows an outline diagram of a system of the invention accordingto a variant of the invention, the system comprising several currentgenerating modules connected to a heat pump module and to severalrefrigeration modules.

FIG. 7 shows an outline diagram of a system of the invention in the casewhere the alternating current generator is a combustion engine connectedto an alternator and the heat pump uses the absorption refrigerationcycle.

FIG. 8 a is a side view, FIG. 8 b a front view and FIG. 8 c a view insection along the plane A-A in FIG. 8 b of a system according to anothervariant of the invention wherein the system comprises a generatingmodule connected to several heat pump modules of various types.

FIGS. 9 a to 9 f show different views of a compression heat pump moduleaccording to the invention comprising two heat pump units provided withthe optional exchanger 15.

FIG. 10 a is a side view, FIG. 10 b a front view and FIG. 10 c as viewin section along the plane C-C in FIG. 10 b of an absorption heat pumpmodule according to the invention.

FIG. 11 a is a side view, FIG. 11 b a front view and FIG. 11 c a view insection along the plane D-D of FIG. 11 b of a generating moduleaccording to the invention.

FIGS. 12 a to 12 f show different views of a refrigeration modulecomprising two refrigeration units.

FIGS. 13 a to 13 f show different views of a mixed heat pump andrefrigeration module.

FIGS. 14 a to 14 c show different views of an example of a system of theinvention comprising a generating module and a mixed heat pump andrefrigeration module.

FIG. 15 shows an example of a system comprising a generating module, amixed heat pump and refrigeration module and a module of therefrigeration module type comprising two refrigeration units.

FIG. 16 shows an example of a system according to the inventioncomprising a generating module, a mixed heat pump and refrigerationmodule, of the refrigeration module type comprising two refrigerationunits and two isothermal modules.

FIG. 17 shows an outline diagram of the compression heat pump unitdesigned according to a first operating mode.

FIG. 18 shows an outline diagram of the compression heat pump unitdesigned according to a second operating mode.

FIG. 19 shows an outline diagram of a fuel cell equipped with areforming unit or reformer, said cell belonging to the generatingmodule.

LIST OF REFERENCES

-   1 System according to the invention-   2 Combustion engine-   3 Heat pump-   4 Liquid or gaseous fuel inlet-   5 Mechanical energy produced by the engine-   6 Heat emitted by the alternating current generator in operation-   7 Energy losses-   8 Heat exchanger for the exchange of heat between the alternating    current generator and very hot water-   9 Very hot water circuit-   10 Pressure reducing valve-   10A Pressure reducing valve A (optional circuit with exchanger 15)-   10B Pressure reducing valve B (optional circuit with exchanger 15)-   10C Pressure reducing valve C (optional circuit with exchanger 15)-   11 Water/refrigerating fluid heat exchanger (evaporator in air    conditioning mode)-   12 Air/refrigerating fluid heat exchanger (evaporator in heating    mode, and condenser in air conditioning mode)-   13 Water circuit—cold-water circuit when the heat pump is in air    conditioning mode-   14 Hot-water circuit-   15 Refrigerating fluid/recovery water circuit heat exchanger-   16 Refrigerating fluid circuit-   16A Suction refrigerating fluid pipe-   16B Liquid refrigerating fluid pipe-   17 Compressor-   18 Alternator-   19 Electric accumulator-   20 Electrical energy-   21 Motor fan-   22 Fuel cell-   22A Reformer-   22B Cell core-   22C Reforming reactor-   22D Desulfurization unit-   22E WGS (water gas shift) unit.-   22F Fuel fluid (natural gas, biogas. etc)-   22G Hydrogen-   22H Electricity-   23 Photovoltaic solar panel-   24 DC to AC converter-   25 Solar energy-   26 Fuel (for fuel cell)-   27 Heat pump using the absorption cycle-   28 Absorber-   29 Generator-   30 Circulation pump-   31 Evaporator of the absorption cycle-   32 Pressure reducing valve for the absorption cycle-   33 Condenser of the absorption cycle-   34 Refrigerating fluid-   35 Absorber-   36 Compression heat pump module-   36A Refrigeration module-   36B Mixed module: heat pump and refrigeration-   36C Isothermal module-   36D Heat pump unit-   36E Refrigeration unit-   37 Absorption heat pump module-   38 Current-generation module-   39 a, b, Collectors connecting the water exchangers-   c, d,-   40 Gas pipes connecting the absorption heat pump modules-   41 Power cable-   42 Regulation cable-   44 Heat pump module frame-   46 4-way valve-   47 Refrigeration compressor-   48 Liquid anti-knock bottle-   50 Liquid reservoir-   51 Absorber-   52 Generator-   53 Refrigerating fluid/absorption-cycle water plate exchanger-   54 Refrigerating fluid/absorption-cycle air plate exchanger-   55 Fuel inlet-   56 Thermal engine unit and alternator thereof-   57 Fuel cell and inverter unit thereof-   58 Connection of external thermal sources-   59 Exchanger for exchange of heat between the current generator and    very hot water-   60 Global system power and regulation cubicle-   61 Power cable for energy feed coming from photovoltaic power-   62 Power cable for electrical network feed-   63 Power cable for sending electrical energy to the network-   64 Current-generating module frame-   65A, 65B Two-way refrigeration valves-   65C, 65D-   66 Refrigerating fluid/air exchanger-   67 Non-return valve on refrigerating fluid circuit-   68 Regulation box-   Pc Compression heat pump module-   Pa Absorption heat pump module-   Pr Refrigeration module-   Pm Mixed module: refrigeration and heat pump-   G Current-generating module-   Ce1, Ce2, Customer inlet manifold-   Ce3-   Cs1, Cs2, Customer outlet manifold-   Cs3

DESCRIPTION OF THE INVENTION Definitions

In the present document, the following meanings should be understood:

Thermodynamic system of the refrigeration or heat pump type: devicecomprising a compressor and several exchangers in which a specifictransfer fluid flows, usually referred to as refrigerating fluid, saiddevice absorbing thermal energy at a first temperature and restoringthermal energy at a second temperature, the second temperature beinghigher than the first.

Geothermal loop: set of pipes placed in the ground typically in avertical or horizontal position and intended to exchange heat betweenthe heating or cooling system and the ground.

Heat exchanger: device intended to transfer heat between severalcircuits.

Transfer fluid: heat-transfer fluid used for transferring heat; theclassic examples are refrigerating fluid, water or, glycolated water,sometimes referred to as brine.

Thermal source or source: by convention, the terms source and thermalload refer to the heating mode. The source is the medium from which heatis extracted in heating mode. This extraction of heat takes place withcertain physical characteristics such as the thermal inertia or theavailable power that characterize the source. It should be noted thatthe term source is improper in coating mode since therein heat issuingfrom the building is in fact discharged.

Thermal load or load: the load is the medium where the heat isdischarged in heating mode. This discharge of heat takes place withcertain physical characteristics such as the thermal inertia or theavailable power that characterize the load, and likewise the load is theplace where the heat is withdrawn in cooling mode.

COP or coefficient of performance: the COP or coefficient of performanceof a system in heating mode is defined as the ratio between theavailable heating capacity to the electrical power consumed by thesystem. In the system according to the invention, “electricalequivalent” COP means the COP that the plant would have if electricitywere used in place of gas or biofuel.

Alternating-current generator: device that generates alternating currenteither directly or by means of an additional converter that transformsthe direct current generated into alternating current.

Combustion engine: an engine which, by combustion, transforms thechemical energy contained in a fuel into mechanical energy.

Internal combustion engine: combustion engine where the combustion ofthe fuel producing the energy necessary for functioning takes place inthe engine itself typically in a combustion chamber.

Photovoltaic solar panel: electrical direct-current generator consistingof a set of photovoltaic cells connected together electrically.

Thermal solar collector: device in which the temperature of a solid,liquid or gaseous medium is increased by total or partial absorption ofsolar radiation.

Fuel cell: device producing electricity by means of oxidation, on oneelectrode, of a reducing fuel (for example hydrogen) coupled to thereduction on the other electrode of an oxidant, such as oxygen from theair.

Detailed Description

The combustion engine 2 of the system according to the invention ispreferably an internal combustion engine; it forms part of thecurrent-generating module G. It is preferably supplied with natural gas.According to requirements, it may also be supplied with other gaseous orliquid fuels such as petrol, fuel oil, kerosene, alcohol, or biofuelssuch as vegetable oils, bioethanol or biogas.

It may be a case of other types of combustion engine, such as externalcombustion engines such as Stirling engines. The alternator 18 connectedto the combustion engine also forms part of the generator G.

The fuel cell 22 of the system according to the invention may be anytype of fuel cell known to persons skilled in the art, typically, butnot exclusively, operating at temperatures below 200° C., but which mayin certain cases reach a temperature of 800° C. to 1000° C. (for examplea fuel cell of the “solid oxide” type) and supplied with a suitablefuel, such as hydrogen, methane or other hydrocarbon mixture such aspetrol or fuel oil. The fuel cell is composed at a minimum of a cellcore 22B supplied with hydrogen (the case of fuel cell cores based onproton exchange membranes) or supplied by the plurality of hydrocarbonfuels already cited (the case of high-temperature cell cores of thesolid oxide type). If the cell of the type based on proton exchangemembranes and hydrogen is not directly available, then the fuel cell 22is then composed of a reformer 22A and a cell core 22B. The role of thereformer is to extract the hydrogen necessary to the cell core from morechemically complex fuels already cited, such as natural gas, methane,biogas or other hydrocarbon mixture. The hydrogen thus extractedsupplies the cell core based on proton exchange membranes.

An example of functioning of a fuel cell 22 with reformer 22A isillustrated in FIG. 19 and will be described below. The fuel 22F (whichmay be natural gas, biogas, etc) undergoes in the reformer 22A a seriesof transformations aimed at extracting hydrogen 22G therefrom, whilelimiting the level of impurities (typically sulfur) and carbon monoxide.For this purpose, the fuel first of all passes through a reformingreactor which, following the addition of water, will extract hydrogentherefrom. In the case of methane, for example, the chemical reaction isof the type CH₄+2H₂O═CO₂+4H₂. The role of the unit 22D is to reduce thesulfur content, since sulfur may affect the behavior of the cell core22B. The unit 22E for its part effects the so-called “water gas shift”transformation, which reduces the carbon monoxide content of themixture, which may also affect the behavior of the cell core. Thechemical reaction in this unit is of the type: CO+H₂O═CO₂+H₂.

The photovoltaic solar panels 23 of the system according the inventionmay be any type of panel known to persons skilled in the art, inparticular the semiconductor constituting the photovoltaic cells may,non-limitatively, be amorphous, polycrystalline or monocrystallinesilicon, a semiconductor organic material or a combination of these. Aplurality of photovoltaic solar panels may be used.

In preferred embodiments, the system according to the invention isreversible, namely it may function in a mode favoring heating by thesupply of hot water at temperature T1 (“heating mode”) or in a modefavoring the cooling by the supply of cold water at temperature T3 (“airconditioning mode”). To do this, a cycle-reversal four-way valve 46(FIG. 8C) is installed on the refrigerating fluid circuit 16. It is alsopossible to have non-reversible systems, in particular for certainrefrigeration applications. When the system is provided with theoptional exchanger 15, it is then possible to simultaneously supply hotwater at temperature T1 and cold water at temperature T3 in variableproportions for each in order to meet the requirements of use. Thecycle-reversal four-way valve 46 is then replaced by four two-wayrefrigeration valves 65A, B, C, D. The pressure reducing valve 10 isthen supplemented by two additional pressure reducing valves, meaningthat the circuit comprises three pressure reducing valves: 10A, 10B,10C.

In the case where the heat pump 3 is reversible, the heat exchangers 11and 12 are reversible exchangers. It should be noted that we have chosento describe in detail the functioning of the system according to theinvention in air conditioning mode. When the heat pump functions inheating mode, the water circuit 13 becomes a hot-water circuit.

In addition, the heat exchanger 11 is preferably a plate exchanger.

With reference to FIG. 1, the heat pump 3 of the system 1 according tothe invention is a module Pc 36 that comprises

one or two sealed closed circuits in which a transfer fluid flows, suchas a refrigerating fluid 16,

at least one compressor 17 per circuit driven by an electric motor,

a pressure reducing valve 10,

a first heat exchanger 11, situated at the suction of the compressor 17when the system is functioning in air conditioning mode,

a second heat exchanger 12, situated at the discharge from thecompressor 17 when the system is functioning in air conditioning mode,

an optional third heat exchanger 15, situated at the discharge from thecompressor 17 when the system is in simultaneous air conditioning andheating mode by recovery of heat.

These components are arranged inside a frame, not shown in FIG. 1.

According to the invention also, the compressor 17 is driven by anelectric motor. This electric motor may be supplied electrically by thefirst current generator and/or by one or more of the other currentgenerators, or by the electrical network, according to the choice madeby the global system regulation method chosen. It is possible to use aDC or AC motor. Using an electric motor for operating the compressor 17(and in particular not driving the compressor 17 directly (mechanically)by the combustion engine 2) has the advantage of being able to usehermetic compressors, thus avoiding the risks of leakage relating to theuse of open compressors. In a particular embodiment, the compressor 17is driven by an electric motor supplied electrically by a combustionengine 2, the necessary electricity being generated by the alternator 18driven by said combustion engine 2.

For the reasons mentioned above, the compressor of the heat pump ispreferably a hermetic compressor. Hermetic compressor means a compressorcomposed of a closed casing, in general a welded steel envelope, insidewhich there are a compression unit for compressing the refrigeratingfluid and a motor that drives the compression unit. It is however alsopossible to use semi-hermetic compressors in which it is possible tohave access to certain internal components during maintenance or anyrepairs.

The heat pump 3 of the system 1 according to the invention can beprovided with a third heat exchanger 15. This exchanger is preferably(like the second heat exchanger 11) a plate exchanger.

The heat pump 3 of the system 1 according to the invention allows theuse of all types of thermal loads known to persons skilled in the artfor heating and air conditioning, such as refreshing heating floors orfan convectors. The loads may also be air processing units for thedehumidification of swimming pools and the treatment of fresh air inpremises, or water circuits in industrial processes requiring the use ofhot water and/or cold water.

In a variant of the invention, the heat pump 3 of the system 1 accordingto the invention may be a heat pump of the air/water type, that is tosay a heat pump using external air and/or extracted air as the heatsource in heating mode or a heat pump of the water/water type, that isto say a heat pump using a water circuit in the external ground as theheat source in heating mode. An advantageous thermal source for the heatpump 3 is a geothermal loop.

The heat exchangers on the source and on the load are adapted to thetype of heat pump and to the type of application according to criteriawell known to persons skilled in the art.

With reference to FIG. 4, the refrigeration unit according to theinvention is a module Pr 36A that comprises:

at least one circuit in which a transfer fluid such as a refrigeratingfluid 16 circulates; the circuit is closed and sealed after finalinstallation of the exchanger 11 (in the factory or on the end site),

at least one compressor 17 driven by an electric motor,

a pressure reducing valve 10,

suction refrigerating fluid pipes 16 a and liquid pipes 16 b intended tobe connected to a heat exchanger 66 by the refrigeration circuit,situated at the suction of the compressor 17. This exchanger is notsituated in the module Pr 36A comprising the compressors 17. It may besituated in an isothermal module 36C, as shown in FIG. 16, or may besituated outside a modular unit according to the invention (typically ina building close to the modular unit). This exchanger makes it possibleto close the circuit and is necessary to the functioning of the system.A module may comprise two circuits independent from the refrigerationpoint of view, and therefore two exchangers 66. Each of these exchangersmay be situated in an isothermal module 36C or outside the modular unitas described above.

a second heat exchanger 12 situated at the discharge of the compressor17.

These components are arranged inside a frame, not shown in FIG. 4.

According to the invention also, the compressor 17 is driven by anelectric motor. This electric motor may be supplied electrically by thefirst current generator and/or by one or more of the other currentgenerators, or the electrical network, according to the choice made bythe global system regulation method chosen. It is possible to use a DCor AC motor. Using an electric motor for operating the compressor 17(and in particular not driving the compressor 17 directly (mechanically)by the combustion engine 2) has the advantage of being able to usehermetic compressors, thus avoiding the risks of leakage relating to theuse of open compressors. In a particular embodiment, the compressor 17is driven by an electric motor supplied electrically by a combustionengine 2, the necessary electricity being generated by the alternator 18driven by said combustion engine 2.

For the reasons mentioned above, the compressor of the heat pump ispreferably a hermetic compressor. Hermetic compressor means a compressorcomposed of a closed casing, in general a welded steel envelope, insidewhich there are a compression unit for compressing the refrigeratingfluid and a motor that drives the compression unit, it is however alsopossible to use semi-hermetic compressors in which it is possible tohave access to certain internal components during maintenance or anyrepairs.

The compressor 17 typically, but not exclusively, has a consumedelectric power of 10 to 30 kW depending on the models and the operatingconditions of the compressor (rotation speed, suction pressure anddischarge pressure). The refrigerating capacity wilt vary from 5 to 80kW according to the operating conditions. However, in order to increasethe available refrigeration capacity, it is preferred to use twocompressors 17 connected in parallel and, in this case, the set of twocompressors wilt have a doubled refrigeration capacity and consumedelectric power.

The refrigeration unit of the system according to the invention can beprovided with a third heat exchanger 15. This exchanger is preferably aplate exchanger.

In the present invention, the refrigerating fluid is preferably chosenfrom hydrofluorocarbons HFCs (for example R134A, R407C, R404A andR4110A) which are the most usual. It can also be envisaged usinghydrocarbons, more particularly propane, as the refrigerating fluid. Itis also possible to use CO₂.

A preferred refrigerating fluid for the system of the present inventionis R134A or 410A for the heat pump. A preferred refrigerating fluid forthe system of the present invention is typically but not exclusivelyR404A for the refrigeration unit. However, the functioning of thepresent invention is not limited to the choice of one of the existingfluids on the market, and other fluids can be envisaged.

The heat pump 3 of the system 1 according to the invention allows theuse of all types of thermal load known to persons skilled in the art forheating and air conditioning, such as refreshing heating floors or fanconvectors. The loads may also be air processing units for thedehumidification of swimming pools and the treatment of fresh air inpremises, or water circuits industrial processes requiring the use ofhot water and/or cold water.

In a variant of the invention, the heat pump 3 of the system 1 accordingto the invention may be a heat pump of the air/water type, that is tosay a heat pump using external air and/or extracted air as the heatsource in heating mode or a heat pump of the water/water type, that isto say a heat pump using a water circuit in the external ground as theheat source in heating mode. An advantageous thermal source for the heatpump 3 is a geothermal loop.

The refrigeration unit 36A of the system 1 according the inventioncomprises an air/air refrigeration circuit, that is to say the air iscooled to a so-called mean refrigeration temperature T4 typicallyenabling fresh foodstuffs to be preserved (cheese, milk, etc) or iscooled to a lower temperature T5 referred to as a low refrigerationtemperature typically enabling frozen food to be preserved. The heatcaptured is typically discharged into the external air by means of thecompressor 17 and the refrigerating fluid/air exchanger 12.

The heat exchangers on the source and on the load are suited to the typeof refrigeration unit and the type of application according to thecriteria generally known to persons skilled in the art.

Optionally, the system 36A can be provided with a heat exchanger 15 fordelivering hot water at temperature T1.

In a particular embodiment, as seen more clearly in FIG. 7, the system 1also comprises a heat pump of modular construction using the absorptioncycle 27, and at least one electric accumulator 19. The module Pa 37 ofsaid heat pump comprises an absorber 28, a generator 29, a circulationpump 30, an evaporator 31 situated at the inlet of the absorber, asuitable pressure reducing valve 32 and a condenser 33 placed at theoutput of the generator, a refrigerating fluid 34 and an absorbent 35.This system forms a second subject matter of the invention. The heatpump using the absorption cycle 27 is based on a reduction in thesolubility of a gas in the refrigerating fluid when the temperatureincreases. Advantageously, the absorbent/refrigerating fluid flow pairsare respectively the ammonia/water pair and the water/lithium bromidepair. The refrigerating fluid is absorbed in a deg C solution of theabsorber 28, and the solution enriched with refrigerating fluid istransferred to the generator 29 by means of the circulation pump 30. Thesolution is heated therein, which causes the separation of therefrigerating fluid and an increase in the pressure and temperature. Therefrigerating fluid flows towards the condenser 33, where it condenses,discharging heat. It then passes through a pressure reducing system 32and reaches the evaporator 31, where it evaporates, absorbing heat. Itthen rejoins the absorber 28, and the cycle recommences.

The heat pumps using the absorption cycle are known per se. They areless used since they are more expensive than heat pumps using themechanical steam compression refrigeration cycle. However, heat pumpsusing the absorption cycle require only a little electrical power,mainly for the auxiliary components and regulation. The major part ofthe energy necessary for the absorption cycle is thermal and comestypically from the combustion of fossil energy in a burner. In thesystem according to the invention, the heat pump using the absorptioncycle 27 can be supplied with thermal energy by any suitable source, inparticular by the heat generated by one of the combustion engines 2, bythe fuel cell 22 or by a thermal solar collector.

In an advantageous embodiment of the invention, the system 1 comprises agenerating module connected to a heat pump module; said systemsimultaneously allows:

cooling of water by the heat pump 3 to a temperature T3,

the heating of water by the heat pump 3 to a temperature T1,

the production of very hot water at a temperature T2 by recoveringthermal energy given off by the current generator (which may be acombustion engine 2 connected to alternator 18) during operation,

the production of electricity.

The system 1 according to this embodiment of the invention also allowsthe production of only one or of two or three elements chosen from coldwater, hot water, very hot water and electricity.

The cold water has a temperature T3 typically between −8° C. and +15° C.(the case of water with glycol added) or between 4° C. and 15° C. (thecase of water). This temperature is preferably between 5° C. and 9° C.

The so-called hot water produced by the heat pump 3 has a temperature T1typically between 20° C. and 60° C., and preferably between 30° C. and60° C.

The so-called very hot water (typically domestic hot water) reaches atemperature T2>T1 typically between 40° C. and 75° C., and preferably55° C. and 75° C.

In another embodiment of the invention, the system 1 comprises agenerating module connected to a refrigeration module; said systemallows simultaneously:

the supply of refrigerating fluid at the thermodynamic conditions(evaporation temperature T4 or T5) enabling, after connection to arefrigerating fluid/air exchanger 66, very cold air to be supplied forrefrigeration applications;

optionally the heating of water to temperature T1;

the production of very hot water at a temperature T2 by recoveringthermal energy given off by the current generator (which may be acombustion engine 2 connected to an alternator 18) during operation,

the production of electricity.

A system 1 comprising one or more heat pump and refrigeration modulesaccording to the invention, therefore makes it possible to provide:

the production of elements from among cold water, hot water, very hotwater or refrigerating fluid at the thermodynamic conditions ofmedium-temperature refrigeration, refrigerating fluid at thethermodynamic conditions of low-temperature refrigeration andelectricity;

the cold water has a temperature T3 typically between −8° C. and +15° C.(the case of water with glycol added) or between 4° C. and 15° C. (thecase of water). This temperature is preferably between 5° C. and 9° C.;

the so-called hot water produced by the heat pump 3 has a temperature T1typically between 20° C. and 60° C., and preferably between 30° C. and60° C.;

the so-called very hot water (typically domestic hot water) reaches atemperature T2>T1 typically between 40° C. and 75° C., and preferably55° C. and 75° C.;

the refrigerating fluid to the thermodynamic conditions ofmedium-average temperature refrigeration has an evaporation temperatureT4 typically between −15° C. and 5° C. and preferably between −10° C.and −5° C.;

the refrigerating fluid to the thermodynamic conditions oflow-temperature refrigeration has an evaporation temperature T5typically between −40° C. and −25° C. and preferably between −35° C. and−30° C.

When the current generator is a combustion engine, possibly associatedwith an alternator, the heat is recovered both on the cooling circuit ofthe combustion engine 2 and on the exhaust gases of the engine.

When the electric current generator is a fuel cell 22, optionallyassociated with a DC to AC converter, the heat is recovered on thecooling circuit of the fuel cell 22 to which a heat exchange circuitplaced on the current converter is optionally added.

When the electric current generator is a photovoltaic solar panel 23,possibly associated with a DC to AC converter, the heat isadvantageously recovered by a heat exchange circuit placed under thephotovoltaic cells, and/or by a heat exchange circuit placed on thecurrent converter. This has a more favorable energy efficiency than theuse of an electric element for heating the water.

The so-called cold water is obtained at a temperature T3<T1 typicallybetween −8° C. and +15° C. (the case of water with glycol added) orbetween 4° C. and 15° C. (the case of water). This temperature ispreferably between 5° C. and 9° C.

In an advantageous embodiment, T1 is between 20° C. and 60° C., T2>T1 isbetween is 40° C. and 75° C., and T3<T1 is between −5° C. and +15° C.

T4<T3 is between −15° C. and 5° C.

T5 is between −45° C. and −25° C.

The system 1 according to the invention is also provided with aregulation system, preferably electronic (not shown, preferably situatedin a so-called power and regulation cubicle which for its part ispreferably situated in the generating module G 38). This regulationsystem can function with several set points, thus making it possible totrigger the functioning of the system according to the inventionaccording to the requirements for cold water at temperature T3, and/orhot water at temperature T1 and/or very hot water at temperature T2, orrefrigerating fluid at temperatures T4 or T5, and to make the choice tooptionally return some of the electrical energy generated by the systemto the external electrical network. It will be described in greaterdetail below.

With reference to FIG. 1, the engine 2 is supplied with fuel by means ofan inlet 4.

Typically, approximately 32% to 37% of the energy supplied to thecombustion engine in the form of fuel is recovered in the form ofmechanical energy 5 in order to drive the alternator 18 and produceelectricity 20. This makes it possible to supply the compressor 17 ofthe heat pump 3 with the electricity 20 thus produced. Any surplus ofelectricity produced by the alternator 18 in the case of a partial toador a sizing for this purpose can be used for recharging the electricaccumulator 19 or be re-injected onto the network.

In addition, the electricity produced by the alternating currentgenerator is used for operating the electrical and/or electronicelements of the system according to the invention, such as solenoidvalves, one or more powered fans 21 associated with the heat exchanger12, and the electronic regulation system. Moreover, some of theelectricity produced by the AC generator can be used for supplyingelectrical apparatus or devices situated outside the system according tothe invention, such as lighting for example.

Typically when the AC generator is a combustion engine 2, approximately40% to 60% of the energy supplied to said engine 2 is recovered in theform of heat energy 6 for heating domestic hot water. The rest of theenergy (typically between 3% and 25%) being dissipated in the form oflosses 7.

Still with reference to FIG. 1, and considering the air condition mode,the heat pump 3 the compressor 17 of which is supplied with electricity20 produced by the alternating current generator supplies cold water 13,with an “air conditioning” COP of between 2.9 and 3.5. The system alsosimultaneously supplies hot water 14, with a heating COP of between 3and 5.

In addition, when the AC generator is a combustion engine 2, at leastone heat exchanger 8 placed on the combustion engine 2 recovers the heat6 emitted by the engine 2.

Preferably at least one heat exchanger (not shown) is placed on theexhaust gas circuit of the engine, and at least one second heatexchanger is placed on the liquid-cooling circuit of the engine 2.

According to the invention, the system 1 is modular in design andcomprises at least one electric current generating module G 38 and oneor more (N) production modules P each comprising one or two heat pumpunits 36D or refrigeration units 36E. The electric current generatingmodule may comprise at least one combustion engine 2.

According to this modular embodiment, each of the N heat pump Pc modulesand/or refrigeration modules Pr (i.e. of the steam compression type) ofthe system 1 according to the invention comprises

a sealed closed circuit in which the transfer fluid circulates, such asa refrigerating fluid 16,

a compressor 17 driven by an electric motor,

a pressure reducing valve 10,

in the case of heat pump units Pc, a first heat exchanger 11, preferablyof the plate type, situated at the suction of the compressor 17 when thesystem is functioning in air conditioning mode,

a second heat exchanger 12, situated at the discharge of the compressor17 when the system is functioning in air conditioning mode,

optionally a third heat exchanger 15, preferably a plate exchanger,

in the case of refrigeration units Pr, a heat exchanger 66 that can besituated in a specific isothermal module forming part of themodular-design system or may be situated at a distance from themodular-design system, in the enclosure of a building.

These components are arranged inside a frame.

The heat pump modules Pc are preferably identical, in particular withregard to the essential components and sizing thereof. This makes itpossible to manufacture them in mass production. This also facilitatesmaintenance and repair thereof, since it is simply possible to exchangea defective module with a module in operating condition and repair thedefective module without its being connected to the system 1.

In general terms, in the context of the present invention, the heat pumpmodule Pc comprises two compression heat pump units 36D, or the mixedmodule Pm comprises a heat pump unit 36D and a refrigeration unit 36D orthe refrigeration module 36A comprises two refrigeration units 36E.These modules are produced in the form of a frame, said frame havingmanifold pipes, optionally a fuel feed pipe, and electric power andregulation cables passing through them. Said frame is also provided withmeans of connecting the various pipes and cables to the system. By wayof example, the dimensions of such a so-called production module frameare: length 1700 mm, width 2200 mm, height 2420 mm.

The frame typically encloses

at least one compressor, advantageously of the variable power type,

at least one reversible battery in V formation,

at least one fan,

at least one plate exchanger,

auxiliary components of a heat pump or refrigeration unit of a knowntype, such as a four-way valve, two-way refrigeration valves, and one ormore refrigeration pressure reducing valves,

a liquid reservoir intended to contain refrigerating liquid.

In general terms, in the context of the present invention, theabsorption heat pump module Pa can be produced in the form of a frame,said frame having manifold pipes, a fuel inlet pipe and electrical powerand regulation cables passing through it. Said frame is also providedwith means of connecting the various pipes and cables to the system.Said frame typically contains at least the following elements:

a refrigerating fluid/water exchanger,

a generator,

an absorber,

a refrigerating fluid/water plate exchanger,

and other auxiliary components of an absorption heat pump, such as: apump, pressure reducing valves.

In general terms, in the context of the present invention, the currentmodule G can be produced in the form of a frame, said frame having afuel inlet pipe and power and regulation cables passing through it. Saidframe is also provided with means of connecting the various pipes andcables to the system. Said frame typically contains at least one currentgenerator of the thermal engine type connected to the alternator thereofor a fuel cell, an exchanger for exchanging heat between the currentgenerator or generators and the very hot water, and a global power andregulation cubicle for the system; optionally, other current generatingsources, such as a fuel cell and optionally the alternator thereof, orother external thermal sources (such as connection to thermal solarcollectors) can be arranged in the same frame of the current generatingmodule. By way of example, but without this being essential, thedimensions of such a generating module frame are: length 2300 mm, width2300 mm, height 2420 mm.

In general terms, in the context of the present invention, thecombustion engine 2 is preferably an engine adapted for natural gas. Itmay for example be an engine with a cubic capacity of 2 liters to 4.6liters of a normal type as used in certain motor vehicles with petrol ordiesel industrial vehicles, but specifically adapted for use withnatural gas. In a preferred variant embodiment of the current generatingmodule, a combination of two engines 2 is used, with identical ordifferent cubic capacities, according to the requirement of the user.

It is advantageous to provide in the system 1 at least one connectionfor an external heat transfer fluid that provides thermal energy, comingfor example from a thermal solar collector or a geothermal loop; thisconnection is advantageously made at generation level since thissimplifies both the design and regulation of the system 1.

In general terms, in the context of the present invention, a singleelectric current generator is advantageously used, but this depends onthe energy sizing of the system. It is possible to use two electriccurrent generators, preferably arranged in the same generating module G;one of these two generators is advantageously a combustion engine 2. Itis possible to use two combustion engines 2, either in the same currentgenerating module or in two separate modules. It is preferred tointegrate them in the same module since this makes it possible to sharecertain components such as the lubrication and/or cooling circuits.

The use of two combustion engines 2 optimizes use thereof according tothe requirements for hot water, very hot water, cold water and generatedelectric current. By way of example, if the two engines are petrol ornatural gas engines, and the energy requirement that they must supply isfairly low, it may be preferable, for the purpose of preserving theservice life of the engines or optimizing the COP thereof, to use onlyone of the two engines, whereas in the case where the two combustionengines 2 are diesel engines, it may be preferable to use both underpartial load rather than one at full load. The existence of two enginestherefore increases the flexibility of use of the system 1 and moreoverprovides redundancy in the event of engine breakdown. It is obviouslypossible also to use more than two engines.

In an advantageous embodiment, use is made of engines of a normal typedeveloped for mass production cars, since this provides a highlyadvantageous purchase price and reliable maintenance.

In a particular embodiment, which may be combined with all the otherembodiments, the alternators are put in contact with a heat exchanger inorder to recover at least some of the thermal energy in which part ofthe electrical energy is transformed, knowing that the energy efficiencyof an alternator is always less than 100%. This heat exchanger thenheats a heat transfer liquid that is entered into a heat pump circuit.

It is also possible to combine in a module firstly a generator composedof a combustion engine and an alternator with another generator of thefuel cell type. It is thus possible to take advantage of theparticularities of each of the generators: lower price for combustionengines, silence in operation and higher energy efficiency for fuelcells.

Finally, when the price of fuel cells has decreased or for particularapplications (industrial sites having available unprocessed hydrogen),two generators of the fuel cell type will be installed.

FIG. 5 illustrates a particular embodiment comprising two cogenerationunits, which may be integrated in the same generating module G,connected to a plurality of heat pump modules of the steam compressionPc type. The various heat pump modules are connected together bycustomer inlet manifolds Ce1, Ce3 and by customer outlet manifolds Cs1,Cs3. Customer inlet pipes Ce2 and customer outlet pipes Cs2 are providedat the very hot water circuit 9. FIGS. 8 a to 8 c illustrate better anexample embodiment of a system comprising several compression heatmodules 36, in this case three modules, connected to two absorption heatpump modules 37, which are for their part connected to a currentgenerating modules 38. These modules 36, 37, 38 are illustratedindividually in FIGS. 9 a to 9 f, 10 a, b, c and 11 a, b, c. In the sideview in FIG. 8 a a frame 44 of the heat pump module 36 or 37 can beseen, which has four manifolds 39 a, 39 b, 39 c, 39 d passing throughit, the diameter of the manifolds being able to be adapted to the waterflows necessary for the application, by power cables 41 and regulationcables 42. The frame 44 forms a housing open on the sides so that it canhave the fluid manifolds and electric cables passing through it, or evenpossibly have gas pipes 40 passing through it if required (for examplein order to connect a distant absorption heat pump module 37 to thegenerating module 39 passing through a compression heat pump module 36).The collector 39 a is a collector for the entry and the collector 39 b acollector for the exit of fluid. The other two collectors 39 c for entryand 39 d for exit are intended for the recovery of heat in airconditioning mode; they are then connected to the third optional heatexchanger 15 present in this variant in the compression heat pump module36, and functioning on the same principle as the exchanger 15 of themodule Pc. In a variant, a third recovery heat exchanger (not shown) mayalso be present in the absorption heat pump module 37.

As mentioned above, the generating module 38 is also produced in theform of a frame 64, forming a housing open on the side so that it canhave the fluid manifolds and electric cables passing through it.

As can be seen more clearly in FIGS. 9 a to 9 f and in FIGS. 8 b and 8c, a compression heat pump module 36 comprises, inside the frame 44thereof, two heat pump units each comprising a fan 21, a refrigeratingfluid/air exchanger 12, a four-way valve 46, a refrigeration compressor17, a liquid anti-knock bottle 48, a refrigerating fluid/water plateexchanger 11, a liquid reservoir 50 and optionally a refrigeratingfluid/recovery water plate exchanger 15, the context of this option, thefour-way valve is replaced by four two-way refrigeration valves 65A,65B, 65C, 65D (FIG. 9 e), the functioning of which will be describedbelow. An absorption heat pump module 37 comprises, inside a frame 44,and as can be seen more clearly in FIGS. 8 a to 8 c and 6 b and 6 c, afan 21, a refrigerating fluid/air exchanger 54, an absorber 51, agenerator 52 and a refrigerating fluid/water plate exchanger 53. Thesemodules 36, 37 function on the same principle as the modules Pc and Pa,as described previously.

The operating principle of a steam compression heat pump unit thatcomposes a heat pump module Pc 36 will now be described in more detailwith reference to FIGS. 17 and 18.

FIG. 17 shows schematically a heat pump unit according to a firstembodiment of the invention, in particular a reversible heat pump with afour-way valve 46. The functioning thereof in heating and cooling modeswill be described hereinafter.

When the heat pump unit of FIG. 17 is functioning in heating mode, theregulation of the machine will satisfy the heating capacity requirementby regulating the power of the refrigeration compressor so as to complywith the hot water temperature T1. Thus all the available heat isdischarged to the water of the heating system through the exchanger 11.The four-way valve 46 connects the discharge pipe of the compressor tothe exchanger 11. The pressure reducing valve 10 regulates the flow ofrefrigerating fluid in order to maintain superheating of this fluid whenit leaves the exchanger 12. The four-way valve 46 connects the exchanger12 to the suction pipe of the compressor 17. The regulation loopconcerns the temperature T1 of hot water leaving the exchanger 11.

When the heat pump unit of FIG. 17 is functioning in cooling mode,regulation of the machine will satisfy the refrigerating capacityrequirement by regulating the power of the refrigeration compressor inorder to comply with the cold water temperature T3. All the heatavailable is then discharged to the external air through the exchanger12. The pressure reducing valve 10 regulates the flow of fluid when itleaves the exchanger 11. The four-way valve 46 connects the dischargepipe of the compressor 17 to the exchanger 12. The pressure reducingvalve 10 regulates the flow of refrigerating fluid to maintainsuperheating of this fluid when it leaves the exchanger 11. The four-wayvalve 46 connects the exchanger 11 to the suction pipe of the compressor17. The regulation loop concerns the temperature T3 of cold waterleaving the exchanger 11.

FIG. 18 shows schematically a heat pump unit according a secondembodiment of the invention, in particular a reversible heat pump with arecovery exchanger 15 and four two-way refrigeration valves (or solenoidvalves) 65A, 65B, 65C, 65D. The functioning thereof according to the sixpossible operating modes thereof will be described below.

When the heat pump unit of FIG. 18 is functioning in cooling mode, themachine will satisfy the refrigerating capacity requirement byregulating the power of the refrigeration compressor 17 in order tocomply with the cold-water temperature T3. All the available heat isthen discharged to the external air through the exchanger 12. Thesolenoid valve 65B is open, all the other solenoids valves being closed.The pressure reducing valve 10A regulates the flow of refrigeratingfluid in order to maintain superheating of this fluid when it leaves theexchanger 11. The pressure reducing valves 10B and 10C are closed. Theregulation loop concerns the temperature T3 of cold water leaving theexchanger 11.

When the heat pump unit of FIG. 18 is functioning in cooling and heatrecovery mode, regulation of the machine will satisfy the refrigeratingcapacity requirement by regulating the power of the refrigerationcompressor in order to comply with the cold-water temperature T3. Theavailable heat is sent to the water recovery circuit by means of theexchanger 15. The solenoid valve 65C is open, all the other solenoidvalves being closed. The pressure reducing valve 10B regulates the flowof refrigerating fluid in order to maintain superheating of this fluidwhen it leaves the exchanger 11. The pressure reducing valves 10A and10C are closed. The regulation loop concerns the temperature T3 of coldwater leaving the exchanger 11.

When the heat pump unit of FIG. 18 is functioning in cooling mode, withrecovery of heat and discharge of heat unused, the regulation of themachine will satisfy the refrigerating capacity required by regulatingthe power of the refrigeration compressor in order comply with thecold-water temperature T3. The available heat is sent to the waterrecovery circuit by means of the exchanger 15. If the quantity of heatavailable is greater than requirements, then the excess is sent to theexchanger 12. The solenoid valves 65B and 65C are open, all the othersolenoid valves being closed. The pressure reducing valves 10A and 10Bregulate together the flow of refrigerating fluid in order to maintainsuperheating of this fluid when it leaves the exchanger 11. The pressurereducing valve 10C is closed. Two parallel regulation loops are inoperation: a first concerning the temperature T3 of cold water leavingthe exchanger 11 and a second that controls the temperature T1 of hotwater leaving the exchanger 15.

When the heat pump unit of FIG. 18 is functioning in heating mode,regulation of the machine will satisfy the heating capacity requirementby regulating the power of the refrigeration compressor in order tocomply with the hot-water temperature T1. The available heat extractedfrom the air by means of the exchanger 12 is sent to the water recoverycircuit by means of the exchanger 15. The solenoid valves 65A and 65Care open, all the other solenoid valves being closed. The pressurereducing valve 10C regulates together the flow of refrigerating fluid inorder to maintain superheating of this fluid when it leaves theexchanger 12. The pressure reducing valves 10A and 10B are closed. Theregulation loop concerns the temperature T1 of the hot water leaving theexchanger 15.

When the heat pump assembly of FIG. 18 is functioning in heating andheat recovery mode, regulation of the machine will satisfy therefrigerating capacity requirement in order to comply with thecold-water temperature T3 (exchanger 11). In addition, the regulation ofthe machine will satisfy the heating capacity requirement by regulatingthe power of the refrigeration compressor in order to comply with thehot-water temperature T1 (exchanger 15). The complementary capacity isextracted from the air by means of the exchanger 12. The solenoid valves65A and 65C are open, all the other solenoid valves being closed. Thepressure reducing valve 10C regulates the refrigerating fluid flow inorder to maintain superheating of this fluid when it leaves theexchanger 12. The pressure reducing valve 10B regulates therefrigerating fluid flow in order to maintain superheating of this fluidwhen it leaves the exchanger 11. The pressure reducing valve 10A isclosed. Two parallel regulation loops are in operation again: a firstconcerning the hot-water temperature T1 leaving the exchanger 15 and asecond concerning the cold water temperature T3 leaving the exchanger11.

When the heat pump unit of FIG. 18 is functioning in defrosting mode,the machine will extract heat at the recovery circuit by means of theheat exchanger 15. This heat will be sent to the exchanger 12 in orderto defrost it. The solenoid valves 65B and 65D are open, the othersolenoid valves being closed. The pressure reducing valve 10C controlsthe superheating of the refrigerating fluid leaving the exchanger 15,the other pressure reducing valves being closed. Regulation of themachine launches the defrosting and stops it on the basis of theinformation given by the pressure and temperature sensors of thecircuit.

As illustrated in FIGS. 11 a, 11 b and 8 b and 8 c, the currentgenerating module 38 has a frame 64, provided with a fuel inlet 55communicating with the pipe 40 of the module 37. The frame 64 comprisesat least one current generator, which may be a combustion engine and thecurrent generator 56 thereof, or a fuel cell with the inverter 57thereof. A connection of the external thermal sources 58 may be providedfor thermal solar collectors or other hot-water sources. An exchanger 59is provided for effecting the exchange of heat between the currentgenerator and the very hot water. The frame 64 also contains a globalpower and regulation cubicle for the system 60, said cubicle beingprovided with connections to power cabling 61 for feeding energy comingfrom a photovoltaic panel, cabling 62 for feed from the externalelectrical network and power cabling 63 for sending electrical energy tothe external electrical network. In a variant, cabling 63′ can connectthe cubicle 60 to the feed of an auxiliary energy source such as comingfrom a wind turbine, a turbine or the like.

FIG. 6 illustrates another particular embodiment comprising twogenerating modules G, 38 connected to a heat pump of the steamcompression type Pc, 36 and to a plurality of refrigeration modules Pr,36A. The various refrigeration modules Pr are connected together andconnected to the heat pump module Pc by customer inlet manifolds Ce3 andby customer outlet manifolds Cs3. The water flows in the modularexchangers are balanced in this case by means of balancing valves of thesystem.

FIGS. 12 a to 12 f illustrate better an example embodiment of arefrigeration module 36A comprising two refrigeration units 36E on acommon frame. More particularly the detail view 12 f illustrates to anenlarged scale the inlet and outlet connection pipes to the cold watercircuit 13, the inlet and outlet connection pipes to the hot watercircuit 14, and the four refrigerating fluid pipes, including two forsuction 16A and two for liquid 16B, for connecting the two refrigerationunits 36E to a refrigerating fluid/air exchanger 66 situated at adistance, being external to the module 36A. FIGS. 12 a and 12 b arefront and rear views of the refrigeration module 36E, FIG. 12 billustrates a side view of a refrigeration module 36A comprising tworefrigeration units 36E, FIG. 12 d is a perspective view of therefrigeration module 36A and FIG. 12 e is a view in section of themodule 36A produced with the plane D-D of FIG. 12 b. As can be seen inthese figures, the refrigeration module 36A comprising two refrigerationunits 36E has total symmetry vertically, which makes it possible toarrange all the components of the two refrigeration units advantageouslyon a common frame of the module.

FIGS. 13 a to 13 f illustrate better an example embodiment of a mixedmodule 36B comprising a refrigeration unit 36E and a heat pump unit 36Don a common frame. More particularly the detail view 13 f illustrates toan enlarged scale the inlet and outlet connection pipes to the coldwater circuit 13, the inlet and outlet connection pipes to the hot watercircuit 14, and the two refrigerating fluid pipes, including one suction16A and one liquid 16B, for connecting the refrigeration units 36E to arefrigerating fluid/air exchanger 66 situated at a distance, beingexternal to the module 36A. FIGS. 13 a and 13 b are front and rear viewsof the mixed module 36B, FIG. 13 b illustrates a side view of a mixedmodule 36B, FIG. 13 d is a perspective view of the mixed module 36B andFIG. 13 e is a view in section produced with the plane E-E of FIG. 13 b.

FIGS. 14 a to 14 c illustrate better an example embodiment of a systemof the invention comprising a generating module 38 connected to a mixedmodule 36B comprising a refrigeration unit 36E and a heat pump unit 36Don a common frame. FIG. 14 a is a side view of the unit, FIG. 14 b is afront view of the unit and FIG. 14 c is a perspective view of thegenerating module unit 38 and mixed module 36B.

FIG. 15 is a front view illustrating an example embodiment of a systemof the invention comprising a generating module 38 connected to acompression heat pump module 36 and to a refrigeration module 36A.

FIG. 16 illustrates an example embodiment of a system of the inventioncomprising a generating module 38 connected to a compression heat pumpmodule 36, to a refrigeration module 36A, connected to a firstisothermal module 36C comprising an evaporator 66 and to a secondisothermal module comprising an evaporator 66.

The main advantages of the system according to the invention comparedwith the systems of the prior art are:

a multi-energy supply or one with several energy sources, typicallyelectricity/natural gas or fuel oil,

functioning as far as a temperature of −20° C. with good efficiency,

a COP on total primary energy superior to 1.5, even when the externaltemperature is low,

integration of the functions within the same modular unit forsimultaneous fluid supply applications (water or refrigerating fluid) attemperatures ranging from −45° C. to +75° C.

As can be seen in FIG. 3, the system according to the invention has anefficiency superior to that of the systems of the prior art, evenrecent, such as condensation gas boilers.

This good efficiency is obtained by the recovery of heat within thesystem:

Firstly, the recovery in the heat pump units by means of the third heatexchanger 15, placed in the refrigerating fluid circuit.

Secondly the recovery of heat in the current generators of thecombustion engine or fuel cell type.

This good efficiency is also obtained by means of the selection ofhigh-performance components: for example generously sized exchangers,combustion engines with a compression ratio optimized for the fuel used,modern variable-speed fans provided with electronic switching motors.

A total power of 60 to 900 kW is typically obtained by means of themodular structure of the system according to the invention, complyingwith the geometric dimensions of a lorry of standard size in Europe(maximum length of the load: 13 meters).

It is moreover entirety possible to achieve all the features describedin the invention, for powers covering the range from 20 to 150 kW, withdimensions allowing passage through a door, i.e. 890 mm wide and 1800 mmhigh. The features described comprise a possibility of obtainingsimultaneously water at three different temperatures T1, T2 and T3 aswell as refrigerating fluid at temperatures T4 and T5.

In a particular embodiment, the steam compression heat pump modulecomprises two heat pump units each comprising a compressor (typicallyspiral compressors, also referred to as scroll compressors), a fan, aV-formation reversible air/refrigerating fluid exchanger (referred to asa “battery”) and two water/circuit refrigerating fluid exchangers(including an optional one for the heat recovery circuit). Theembodiment will be illustrated below by examples.

In air/water mode, the heat pump module can function in heating modealone or air conditioning alone with possible recovery on an independentcircuit. Thus, in winter, the battery on the air is in evaporator mode,while the plate exchanger functions in condenser mode. For theproduction of hot water at temperature T1, additional heat may ifnecessary come from the heat recovered on the cooling circuit of thecombustion engine and on the exhaust fumes thereof.

It is also possible to recover the heat from the engine at very hottemperature T2. In summer, the battery on the external air functions incondenser mode, whereas the plate exchanger functions in evaporatormode. This allows the production of cold water, and offers thepossibility of also providing hot water at temperature T2 on anindependent circuit by virtue of the recovery on the cooling circuit ofthe combustion engine and on the exhaust gases thereof.

In heating mode alone, the heat pump heats the water partly, and therecovery of heat on the cooling of the combustion engine and the exhaustgases thereof provides if necessary the additional heat, in order tosupply for example water at a typical temperature of 45° C.

In air conditioning mode, the heat pump module cools the cold water, forexample to a temperature of 7° C., whereas independently it is possibleto generate hot or very hot water by recovering the heat generated bythe electrical energy generating module (combustion engine), accordingto the requirements of the consumer.

In water/water mode, the system can produce simultaneously hot water forheating and cold water for air conditioning, both in summer and inwinter. Then the batteries on the external air are no longer used, butonly the reversible plate exchangers: one functions in condenser mode toproduce hot water, the other functions in evaporator mode to producecold water. The recovery of heat on the electrical energy generatingmodule is used for additional heat on the production of hot or even veryhot water (domestic water).

In an advantageous embodiment, which can be implemented with all theother embodiments and variants thereof, the system 1 is controlled by atleast one computer machine comprising at least one microprocessor and atleast one data entry interface. Data are entered in the microprocessorof said computer machine by means of said data entry interface.

The invention also concerns a method of regulating a system 1 accordingto the invention. This regulation mode is described here.

In a first step (a), at least one so-called “basic data item” is enteredin said microprocessor. These basic data are typically entered in theprocessor either at the initial programming thereof in the factory, orwhen the system 1 is commissioned on the site of the user(parameterizing of the regulation for the given installation) or againby the user over the course of time during the use of the system 1(level-one parameterizing to take account of basic changes, for examplethe cost of the energy).

These basic data concern the technical features of the modules and thecomponents and consumables thereof. They are selected from the groupformed by:

(da1) the unit cost of the fuel of each combustion engine 2, fuel cell22 and absorption heat pump used in the system 1;

(da2) the energy content of each fuel;

(da3) the CO₂ impact of each fuel per unit of mass;

(da4) the energy efficiency of each combustion engine 2 according to theload and rotation speed thereof, which makes it possible to determinethe quantity of CO₂ discharged per unit of mechanical power produced bythis combustion engine 2;

(da5) the nominal power at full load of each combustion engine 2according to the rotation speed thereof;

(da6) the thermal output percentage recovered on the cooling circuit ofthe engine and the thermal output percentage recovered on the exhaustgases, which makes it possible to determine the quantity of CO₂discharged per unit of thermal output produced by the combustion engine2,

(da7) the unit cost of the electrical energy supplied by the externalnetwork (instantaneous cost, change thereof as a function of time, andchange thereof as a function of the power level demanded);

(da8) the service life of each generator (mainly of the combustionengine 2 and fuel cell 22) according to the load thereof;

(da9) the maintenance cost for each generator (mainly the combustionengine 2 and fuel cell 22) according to the number of operating hours;

(da10) the cost of dismantling and replacing each generator(mainly thecombustion engine 2 and fuel cell 22);

(da11) the service life, maintenance cost and cost of dismantling andreplacing each type of heat pump (using the steam compression cycle orusing the absorption cycle);

(da12) the efficiency of the alternator as a function of the electricalpower that it supplies, which makes it possible to determine themechanical power demanded of the combustion engine 2 for an electricalpower supplied;

(da13) the efficiency of the fuel cell 22 as a function of the loadthereof when it is not equipped with a reformer (the typical hut notexclusive case of a cell of the PEM type—Proton Exchange Membranesupplied by hydrogen), or the efficiency of the fuel cell as a functionof the load thereof when it is equipped with a reformer (the typicalcase of a PEM cell supplied by a fuel other than hydrogen);

(da14) the efficiency of the inverter of the fuel cell 22 orphotovoltaic solar panels 23 when such exist;

(da15) the electrical consumption and the fluid flow (typically glycol)of the circulation pump of the solar collectors;

(da16) the unit selling price of the electrical energy supplied to theexternal network,

(such as the instantaneous price, the change thereof as a function oftime and the change thereof as a function of the power level demanded).

In an advantageous embodiment, there are entered for each type of heatpump the performance tables giving the refrigerating capacity supplied,the heating capacity supplied, the electrical power consumed, and thequantity of fuel consumed if applicable (the case of the absorption heatpump) within the operating range thereof. These performance tables aredefined in fact by the water temperatures of each circuit (T1, T2 andT3, T4 and T5), the fluid flow of the associated exchangers, and theinput temperature of the ambient air. The regulation mode may providethat any functioning with one or more of these parameters outside theoperating range defined is prohibited.

In an advantageous embodiment, there are entered, for each compressorused in the steam compression heat pumps, by way of supplementarycontrol, the following basic data:

the performance tables giving the refrigerating capacity supplied,

the heating capacity supplied,

the electrical power consumed as a function of the suction pressure anddelivery pressure of the compressor for a given refrigerating fluid.

These data enable the above performance tables to be crosschecked. Theycan also be used as basic data for determining, for the complete system,the refrigerating and heating capacities supplied as well as theelectrical power consumed by the steam compression heat pumps. Thesedata include, for each compressor, the volumetric flow level (expressedtypically as a percentage) at which it functions (typically 10% to100%).

In a second step (b), at least one so-called “instantaneous data item”is entered. These instantaneous data are typically entered in themicroprocessor during functioning thereof by the measuring equipmentthat the various components of the system 1 have, or by a deviceexternal to the system 1 (for example by an electrical contact of the“peak day cancellation of the electrical system”, by an Ethernetnetwork, etc) communicating some of these data to the plant.

This at least one instantaneous data item is selected from the groupformed by:

(db1) the instantaneous electrical power produced by each currentgenerator present: alternator 18, fuel cell 22, photovoltaic solar panel23;

(db2) the rotation speed of each combustion engine 2;

(db3) the instantaneous fuel consumption of the plant (explosion engineand absorption heat pump);

(db4) the temperature of the fluid recovering the thermal energy fromthe combustion engine 2 (in particular the thermal energy contained inthe cooling circuit and in the exhaust gases);

(db5) the instantaneous electrical power consumed by the system 1 fromthe network, obtained by direct measurement;

(db6) the instantaneous power supplied to the network by the system 1,obtained by direct measurement;

(db7) the current, voltage or instantaneous electrical power produced bythe photovoltaic solar panel 23 (if such panel is present);

(db8) the instantaneous temperature T1;

(db9) the instantaneous temperature T2;

(db10) the instantaneous temperature T3;

(db11) the instantaneous temperature T4;

(db12) the instantaneous temperature T5;

(db13) the temperature of the ambient air;

(db14) the number of operating hours of each electric current generator(mainly combustion engine 2 and fuel cell 22);

(db15) the number of operating hours of each heat pump circuit in theplant (steam compression or absorption type).

If one of the instantaneous temperatures T1, T2 or T3 is selected (datadb8, db9, db10), it is advantageous to select all three.

In a third step (c), at least one so-called “target data item” isdefined, to which a so-called. “target value” is allocated, said targetdata item being selected from the group formed by:

(dc1) the temperature T1 and the change thereof as a function ofparameters such as the external temperature or the energy cost (theideal comfort may give Way to economically acceptable comfort);

(dc2) the temperature T2 and the change thereof as a function ofparameters such as the external temperature or the energy cost;

(dc3) the temperature T3 and the change thereof as a function ofparameters such as the external temperature or the energy cost;

(dc4) the temperature T4 and the change thereof as a function ofparameters such as the required temperature in the external refrigeratedenclosure or the energy cost;

(dc5) the temperature T5 and the change thereof as a function ofparameters such as the required temperature in the external refrigeratedenclosure or the energy cost;

(dc6) the global COP as being the maximum global COP for the system 1,this point being correlated with the minimum global CO₂ impact of thesystem 1;

(dc7) the energy cost as being the minimum energy cost of the system 1;

(dc8) the total operating cost as being the total minimum operating costof the system 1.

Whatever the target data item or items chosen, there may in addition bea supplementary target data item such as the minimum electric power tobe supplied to the network (in the case of operation as an emergencygenerator for example).

Said at least one target data item and the associated target valuethereof are entered in the microprocessor.

In a fourth step (d), the system 1 is regulated by means of saidcomputer machine so as, for each of the selected target data, to achievethe target value or values determined, said regulation being efThcted bycomparing the current value of the selected target data item, which isdetermined from time to time or regularly or continuously, taking intoaccount the basic data selected as well as the instantaneous dataselected, and adjusting at least one so-called “adjustment data item”selected from the group formed by

(dd1) the type and number of current generators in operation and theelectrical power supplied by each of said generators (advantageously byselecting the generators according to the features thereof vis-a-vis theselected target data);

(dd2) the allocation of the electrical powers supplied by the generatoror generators respectively to the plant and to the network external tothe system 1;

(dd3) the type and number of heat pumps and/or refrigeration units inoperation;

(dd4) in the case of steam compression heat pumps and/or refrigerationunits, adjustment of the volumetric flow (expressed as a percentage)imposed by the regulation on the compressors in order to optimize thesystem 1

so as, for each target data item selected, to bring its current valueclose to the target value.

In the case where. several target data are selected, the regulationmethod may comprise a weighting algorithm for determining a targetparameter from the target values.

Three examples for such a regulation method are given here:

1) If the target data item is the maximum global COP of the system 1, orthe minimum CO₂ impact thereof (data item dc4), it will be sought amongother things to follow the following rules:

it will he sought to operate the current generators in the maximumefficiency region thereof (at full load for example for a combustionengine 2 operating on natural gas);

it will be sought to recover the maximum calorific thermal discharge ofthe combustion engine 2. For example, if the requirements of the plantsite for very hot water are less than the production of the combustionengine 2, this heat production will be totaled with the hot watersupplied by the heat pump modules;

it will be sought to operate all the heat pump modules under partialload rather than to stop some of them so as to reduce the load on eachexchanger and thus provide more effective functioning from an energypoint of view.

2) if the priority target data item is the energy cost as being theminimum energy cost of the system 1 (data item dc5), the approach issimilar to the optimization of the previous example but theparameterisable coefficients for each type of energy become thefollowing:

Purchase cost of each energy external to the system 1 (typicalelectrical energy issuing from the network or energy of the fossil fuelor biogas fuel type) at the time of use. (For example, the cost of theelectrical energy may vary according to the period of the year but mayalso as a function of consumption thresholds in the day or in the year:this threshold or thresholds being related to the electricalsubscription of the plant in question. These weightings may of coursechange in the course of the life of the plant and are thereforeparameterisable in the context of the global regulation method for thesystem).

The price of any resale to the electrical energy network that may ifnecessary be produced by the generating module or modules of the device(this price may also vary, according to rules in general similar tothose that apply to the purchase cost of the electrical energy).

The taking into account of the change in target data such as thetemperatures T1, T2, T3 and the possible change therein as a function ofthe energy costs.

It will be sought to regulate the data listed at (d) (data dd1 to dd4)in order to obtain a minimum cost taking account of the energies soldand purchased.

3) If the priority data item is the total operating cost (data item dc6)as being the minimum total operating cost of the system 1, the approachis similar to the previous optimization but also takes into account:

the service lives of each generator (data item da8),

the maintenance costs (data item da9),

the cost of dismantling and replacing each generator (data item da10),

the cost of dismantling and replacing each type of heat pump (data itemda11).

Particular importance is thus granted to the service life of certaincritical components such as the combustion engines or fuel cells.

The system according to the invention can be used advantageously inbalneotherapy or thalassotherapy equipment, in shared housing, forheating swimming pools, in hospitals or medical establishments, inhotels or tourist accommodation.

The system may also be used advantageously in agricultural applicationswhere there is a need for heating capacity, and possibly refrigeratingcapacity, or even both simultaneously. The primary fuel of the systemcould then be natural gas or biogas but it could also be biogas issuingfrom any biomass that is available, or even optionally generated on theactual site of the application. A first series of applicationspreferably concerns agricultural greenhouses using for example naturalgas as the primary fuel,

A second series of applications concerns methanization units, the systemof the invention then using the biogas produced on site.

The system according to the invention is also used in industrialprocesses requiring the simultaneous heating and cooling of water, usedat different points in the process. This is the case for example withcertain food processes.

The system according to the invention is also used in industrialprocesses requiring the cooling of air to medium and low refrigerationtemperatures used at different points in the process. This is the casefor example with certain food processes, in particular in applicationsof the supermarket type.

Another advantage of the system according the invention is theflexibility of design and flexibility of use thereof. The flexibility ofuse continuously affords an optimum choice of the type or types ofenergy used and/or supplied, according to external parameters and targetparameters (objectives), by means of a suitable regulation method.

The flexibility of design allows optimization of the device according tothe foreseeable requirements of the user, in particular in terms ofthermal capacity, and requirements for different water temperatures.This optimization is made in particular by the choice of the type andnumber of heat pump modules, and by the choice of the type and number ofthe electrical generating module.

The flexibility of design takes account among other things of thefollowing parameters:

a) Requirements for heating capacity and refrigerating capacity andsimultaneous heating capacity and refrigerating capacity of the siteconcerned throughout the year, These parameters will have a directimpact on quantity of heat pump modules concerned and on the choice ofthe cycle employed.

b) Potential requirement for an electrical generator on the plant (as asolution of backup for the network for example). The generating moduleor modules that can be integrated in the device, combined with theflexibility of use of the device, meet this requirement. The choice ofthe generating module or modules will depend among other things on: thepower necessary for supplying the device; the existence of expensiveelectrical thresholds on the site (for example purchase of atransformer, consumption thresholds) that it will then be advantageousnot to cross, characteristics of the site (existence of renewable energyof the wind or photovoltaic type), the required noise level or therequired efficiency (advantage of the fuel cell).

c) Familiarity of the users with one or other of the heat pump devicecycles compression or absorption) and the refrigeration cycle.

d) CO₂ impact: importance of the CO₂ impact of the plant in question(conformity with a label of the HQE (High Environment Quality) type forexample) and valorization of the CO₂ impact of the electrical energy ofthe network.

e) Finally of course, and for all the modules, the optimum configurationwill depend on the initial purchase cost and the operating costs (takingaccount of the energy consumption and maintenance).

It can be noted that the device offers a combination of design solutionsfor adapting effectively to each case.

The flexibility of use takes account in particular of the multiplicityof energies able to supply the various components of the system 1according to the invention, as well as the multiplicity of energy flowsable to be produced by the system 1. All the above modules are suppliedby one or more of the following energies: fossil filets (in particularnatural gas, liquefied petroleum gas, diesel oil, petrol), biofuels,hydrogen and electric current. The heat pump modules may have recoursetypically to the following two conventional cycles: the mechanical steamcompression refrigeration cycle and the absorption cycle. Theconventional water systems connected to the heat pumps can besupplemented in the device by a water system issuing from thermal solarcollectors. The electricity generating modules can have recourse tovarious technologies of the thermal engine and alternator type,photovoltaic solar panel 23, wind turbine, turbine or fuel cell.

The flexibility of use is made possible by virtue of the globalregulation method for all the modules of the device (heat pump andelectrical generators), which takes optimum account among other thingsof the following target parameters (objectives):

(i) Priority given to the COP of the installation. Parameterisablecoefficients will make it possible to express the various energiesexternal to the device (for example the electricity from the network,the thermal energy from the solar collectors and the photovoltaicelectrical energy) in terms of primary energy and CO₂ impact in order togive a global view of the COP of the multi energy device. The globalregulation of the device will take account, in the global optimization,of the efficiency of each type of generating module. Thus, and amongother operating rules:

It will be sought to operate the current generators in the maximumefficiency zone thereof (at full load for example for a thermal enginefunctioning with natural gas);

The maximum heat discharge of the thermal engine will be recovered. Forexample, if the requirements of the plant site for very hot water areless than the production of the thermal engine, this heat productionwill be totaled with the hot water supplied by the heat pump modules;

It will be sought to operate all the heat pump modules under partialload rather than to stop some in order to reduce the load on eachexchanger and thus to afford functioning that is more effective in termsof energy.

(ii) Priority given to the energy operating cost of the plant:

The approach is similar to the previous optimization but theparameterisable coefficients for each type of energy become as follows:

Purchase cost of each energy external to the device (typicallyelectrical energy issuing from the network or energy of the fossil fuelor biogas type) at the moment of use. For example, the electrical energycost may vary according to the time of year but also according to theconsumption thresholds in the day or in the year, this threshold orthresholds being related to the electrical subscription of the plant inquestion. The weightings may of course change over the life of the plantand are therefore parameterisable in the context of the globalregulation method of the device.

Price of any resale to the electrical energy network may if necessary beproduced by the generating module or modules of the device. This pricemay also vary, according to rules in general similar to those that applyto the purchase cost of the electrical energy.

(iii) Priority given to the total operating cost of the plant (inparticular the energy cost, the maintenance cost, which includes inparticular the dismantling cost and the replacement cost). Particularimportance is thus accorded to the service life of certain criticalcomponents such as the combustion engines 2 or the fuel cell 22.

The result of the above is that it is by virtue of its modular design,the very wide temperature range available for respective power rangesfor each temperature sized on use, finally combined with the globalregulation thereof, which knows precisely the functioning andperformances of each of these modules, that the device allowsoptimization of functioning, which is at the same time global, suited tothe complexity of the problems encountered and to changes therein.

EXAMPLES

The example embodiments that follow illustrate certain embodiments ofthe invention. They do not limit the invention.

In these examples, use is made of two types of thermal engine forautomobiles adapted to function with natural gas: one engine with acubic capacity of 2.0 liters manufactured by Volkswagen and another witha cubic capacity of 4.6 liters, manufactured by MAN.

Five different electric current generating modules (module G) weremanufactured:

(a) 2.0 liter engine alone, (b) 4.6 liter engine alone, (c) two 2.0liter engines, (d) two 4.6 liter engines, (e) one 2.0 liter engine andone 4.6 liter engine.

A single heat pump module model (module P) was manufactured, whichcomprised among other things:

two spiral compressors (also referred to as scroll compressors)functioning with R410a fluid, including one with variable power (digitalcontrol);

two fans;

two reversible batteries in V formation;

four dual-circuit reversible-plate exchangers (including two for theoptional recovery circuit).

These P modules, according to the use thereof, can also comprise abuffer tank, an expansion tank, a circulator, and refrigeration andhydraulic valves. The auxiliary components are supplied by the externalelectrical network. The compressors are supplied either with theelectrical energy generating by the module, or by the externalelectrical network.

1-16. (canceled)
 17. A system configured to simultaneously produceelectricity, water at a first temperature, water at a second temperaturegreater than the first temperature, and water at a third temperaturegreater than the second temperature, the system comprising: acurrent-generating module configured to simultaneously produce theelectricity and the water at the third temperature, thecurrent-generating module including an energy producing deviceoperatively connected to a first heat exchanger which is configured toproduce the water at the third temperature; and a unit in communicationwith the current-generating module and configured to receive a portionof the electricity produced by the current generation module and therebysimultaneously produce the water at the first temperature and water thesecond temperature.
 18. The system of claim 17, wherein: the firsttemperature is in a range between one of −8° C. and +15° C. and 4° C.and 15° C.; the second temperature is in a range between 20° C. and 60°C.; and the third temperature is in a range between 40° C. and 75° C.19. The system of claim 17, wherein: the first temperature is in a rangebetween 5° C. and 9° C.; the second temperature is in a range between30° C. and 60° C.; and the third temperature is in a range between 55°C. and 75° C.
 20. The system of claim 17, wherein the energy producingdevice comprises at least one of a fuel cell and solar panel operativelyconnected to a DC-to-AC converter.
 21. The system of claim 20, whereinthe fuel cell comprises: a reformer which transforms fuel received bythe fuel cell to extract hydrogen therefrom; and a cell core whichreceives the hydrogen extracted by the reformer and uses the hydrogen toproduce electricity.
 22. The system of claim 17, wherein the energyproducing device comprises an combustion engine operatively connected toan alternator.
 23. The system of claim 17, wherein the unit comprises aheat pump unit configured to operate under a steam compressionrefrigeration cycle, the heat pump unit including a fluid circuitthrough which a fluid flows, a fluid compressor, a second heat exchangersituated at a suction of the fluid compressor when the system isfunctioning in an air conditioning mode, a third heat exchanger situatedat a discharge of the fluid compressor when the system is functioning inan air conditioning mode, and a fourth heat exchanger situated at thedischarge of the fluid compressor when the system is in a simultaneousair conditioning and heating mode.
 24. The system of claim 23, whereinthe fluid compressor comprises a hermetic fluid compressor.
 25. Thesystem of claim 23, wherein the heat pump unit further comprises apressure reduction valve provided at the fluid circuit.
 26. The systemof claim 17, wherein the unit comprises a refrigerator unit configuredto operate under a steam compression refrigeration cycle, therefrigerator unit including a fluid circuit through which a fluid flows,a compressor driven by an electric motor and in communication with thefluid circuit, a pressure reducing valve in communication with the fluidcircuit, a second heat exchanger provided at a discharge of thecompressor and in communication with the fluid circuit, and a third heatexchanger provided at the discharge of the compressor and incommunication with the fluid circuit.
 27. The system of claim 26,further comprising; a fourth heat exchanger provided at the suction ofthe compressor outside of the refrigerator unit and in communicationwith the fluid circuit.
 28. The system of claim 17, wherein the unitcomprises a heat pump unit configured to operate under an absorptioncycle, the heat pump unit including an absorber, a steam generator, acirculation pump, an evaporator provided at an inlet of the absorber, apressure reducing valve provided at an output of the steam generator, acondenser each provided at the output of the steam generator, and arefrigerating fluid which flows through the heat pump unit.
 29. A systemconfigured to simultaneously produce electricity, water at a firsttemperature, water at a second temperature greater than the firsttemperature, and water at a third temperature greater than the secondtemperature, the system comprising: a current-generating moduleconfigured to produce the electricity, the generating module including afirst heat exchanger configured to produce the water at the thirdtemperature, and an electric accumulator operatively connected to thealternator; and a unit in communication with the current-generatingmodule and configured to receive electricity produced by the currentgeneration unit, the unit comprising a plurality of second heatexchangers configured to produce the water at the first temperature andthe water at the second temperature.
 30. The system of claim 29, whereinthe unit comprises one of: a heat pump unit, the heat pump unitincluding a refrigerating fluid circuit through which a refrigeratingfluid flows, a fluid compressor, a pressure reducing valve and theplurality of second heat exchangers; and a refrigerator unit, therefrigerator unit including a refrigerating fluid circuit through whicha refrigerating fluid flows, a fluid compressor driven by an electricmotor and in communication with the refrigerating fluid circuit, apressure reducing valve in communication with the refrigerating fluidcircuit, and the plurality of second heat exchangers.
 31. The system ofclaim 30, wherein: the first temperature is in a range between 5° C. and9° C.; the second temperature is in a range between 30° C. and 60° C.;and the third temperature is in a range between 55° C. and 75° C. 32.The system of claim 30, wherein the system is also configured tosimultaneously heat the refrigerating fluid at a first evaporationtemperature and at a second evaporation temperature greater than thefirst evaporation temperature.
 33. The system of claim 30, furthercomprising; a third heat exchanger provided outside of the refrigeratorunit and in communication with the refrigerating fluid circuit.
 34. Asystem configured to simultaneously produce electricity, water at afirst temperature, water at a second temperature greater than the firsttemperature, and water at a third temperature greater than the secondtemperature, the system comprising: a plurality of current-generatingmodules collectively configured to produce the electricity and the waterat the third temperature, each current-generating module including afirst heat exchanger configured to produce the water at the thirdtemperature; and a plurality of units in communication with thecurrent-generating modules and configured to receive electricityproduced by the current generation modules, each unit comprising aplurality of second heat exchangers collectively configured to producethe water at the first temperature and water at the second temperature.35. The system of claim 34, wherein each unit comprises one of: a heatpump unit, the heat pump unit including a refrigerating fluid circuitthrough which a refrigerating fluid flows, a fluid compressor, apressure reducing valve and the plurality of second heat exchangers; anda refrigerator unit, the refrigerator unit including a refrigeratingfluid circuit through which a refrigerating fluid flows, a fluidcompressor driven by an electric motor and in communication with therefrigerating fluid circuit, a pressure reducing valve in communicationwith the refrigerating fluid circuit, and the plurality of second heatexchangers.
 36. The system of claim 34, wherein the energy producingdevice comprises one of: at least one of a fuel cell and solar paneloperatively connected to a DC-to-AC converter; and an combustion engineoperatively connected to an alternator.